Blade for a water turbine

ABSTRACT

A turbine blade is described which includes a blade root;a blade tip; a leading edge extending from the blade root to the blade tip; a trailing edge extending from the blade root to the blade tip; a blade root chord defined as a straight line between the leading edge and the trailing edge at the blade root; a blade tip chord defined as a straight line between the leading edge and the trailing edge at the blade tip; wherein the blade tip chord is angularly displaced from the blade root chord by a twist angle of between 50° and 90°.

FIELD OF INVENTION

The present invention relates to turbine blades for water-driven turbines, as well as the turbines themselves, their component parts, and to methods for generating power using the blades and the turbines.

BACKGROUND

Turbines are used to harness power from water flow by using the water flow to move a turbine rotor and generate power. Turbine blades are traditionally straight blades that extend perpendicular to the central axis of the turbine. Turbines can be uses to generate power from wind or water movement such as current and tidal flow.

There are many different blade shapes and profiles presently in use but not all blades perform in the same manner in differing turbine applications. For marine turbines, technology developed for wind power generation has typically been adopted. As seawater is much denser than air, there are opportunities to generate significantly more power from marine turbines.

With a straight blade, since the velocity of the blade tip is much greater than that of the blade root, as fluid flows over the blade, the distribution of force applied to the blade can vary significantly from the blade root to the blade tip. This inhibits the efficiency of the blade resulting in less than optimal power generation from a given fluid flow.

For these and other reasons, known central axis water turbines do not provide optimum usable power output in typical water flow conditions.

The present invention seeks to ameliorate one or more of the abovementioned disadvantages.

SUMMARY OF THE INVENTION

According to a first aspect of the present invention there is provided a turbine blade comprising:

a blade root;

a blade tip;

a leading edge extending from the blade root to the blade tip;

a trailing edge extending from the blade root to the blade tip;

a blade root chord defined as a straight line between the leading edge and the trailing edge at the blade root;

a blade tip chord defined as a straight line between the leading edge and the trailing edge at the blade tip;

wherein the blade tip chord is angularly displaced from the blade root chord by a twist angle of between 50° and 90°.

Preferably, the blade tip chord is angularly displaced from the blade root chord by a twist angle of between 60° and 80°. Further preferably, the blade tip chord is angularly displaced from the blade root chord by a twist angle of between 65° and 75°.

Further preferably, the blade tip chord is angularly displaced from the blade root chord by a twist angle of about 70°.

The blade according to the present invention is particularly suited for use in marine turbines.

The blade can be manufactured from any suitable material utilising a mould process using fibre reinforced plastics or other compounds, but can alternatively be fabricated using structural ribs and sheet skin from steel, non-ferrous alloys or fibre reinforced plastics. Preferably, the blade is made of composite material.

In a second aspect, the present invention provides a fluid driven turbine including a turbine blade according to the first aspect of the present invention.

Preferably, the turbine is a marine turbine adapted to generate power from movement of water in a river or ocean current or tide flow.

In accordance with a third aspect of the present invention, there is provided a central axis water turbine including:

a turbine body having a central axis;

a rotor mounted on the turbine body for rotation about the central axis, the rotor comprising a central hub supporting a plurality of blades, each blade including features of the first aspect of the present invention and extending from a blade root mounted on the hub to a blade tip;

a generator driven by the rotor; and

a housing surrounding the rotor and adapted to direct water flow towards the rotor.

Preferably the blades are raked or tilted or splayed rearward or downstream from the blade root to the blade tip by a tilt angle of about 1° to 20° from a plane perpendicular to the central axis.

Preferably, the housing converges from a front opening forward of the rotor to a narrower throat adjacent the turbine body.

Preferably the blades are splayed rearward from the blade root to the blade tip by a tilt angle of 2° to 10°, and more preferably by 4° to 6° from the plane perpendicular to the central axis. Further preferably, the blades are splayed rearward from the blade root to the blade tip by a tilt angle of about 5° from the plane perpendicular to the central axis.

The rotor preferably includes a nose cone mounted on the front of the rotor to reduce drag on the rotor and reduce turbulent water flow through the housing.

Preferably the nose cone is hollow to provide space for auxiliary systems such as control system or reservoirs for auxiliary or even primary systems.

In a preferred embodiment, the generator is housed with the rotor, the generator being adapted to generate electrical power from the rotation of the rotor. Preferably the generator is directly connected to a shaft. Preferably the generator is connected to the shaft by a splined connection.

Preferably, the generator is driven directly by the rotor, and this arrangement may suit the input speed required by selected generators such as multi-pole or high-pole electric generators. However, in some arrangements it may be suitable to connect a gearbox to the shaft or generator so that the rotation speed of shaft input to the generator is converted to a rotation speed that suits other types of generator.

The blades can be of any cross-sectional shape such as an aerofoil, or tapered or trapezoidal, rectangular, parallel, curved or twisted. In preferred arrangements the aerofoil shape is a NACA 4412 series cross-sectional shape.

Further, it will be appreciated that any blade shape is suitable and that a downstream or rearward tilt or rake angle of 1° to 20° can improve the power output of a central axis turbine having a suitable housing compared with the same turbine with a rake angle of 0° (i.e. with no rake or tilt).

Preferably support struts are provided to support the rotor and generator. Preferably the support struts are hollow to provide ducts or reservoirs. In one arrangement the support struts extend substantially radially between the rotor and generator. In preferred embodiments, a generator end of the support strut is mounted so that the support strut extends substantially tangentially to the generator. This is to improve torque transfer between the generator and the housing, facilitating lighter support struts. Furthermore, an advantage of this preferred arrangement is that fatigue loads on the support struts are reduced since the tangentially-mounted support struts are never disposed completely behind, or completely “shadowed” by the radially-mounted blades when in use.

Preferably a brake is provided, in use to inhibit rotation of the rotor. Preferably the brake is a fail-safe mechanism. Preferably in use a braking actuator holds a brake element remote from the rotor against an actuation force when power is applied to the brake element. In use, when power is removed from the braking actuator, the actuation force, which may be from a spring or utilising some appropriate other kind of urging force, overcomes the braking actuator's force and applies the braking element to the rotor, slowing or stopping the rotation of the rotor.

Preferably a boot or a plug is provided at the blade root to cover any gaps or bumps or bolt heads and the like to minimise interference drag in that region.

Preferably, the housing defines a flow channel having a flow restriction. Advantageously, this arrangement increases the velocity of liquid flowing through the flow channel in a restricted part of the flow channel, relative to an unrestricted part of the flow channel. The flow restriction preferably comprises a venturi, which may form part or the entire flow channel. In particular, the venturi may comprise a divergent-convergent-divergent venturi, tapering from openings at either end of the flow channel towards an inner part of the flow channel.

Preferably the housing is substantially symmetrical about the rotor.

The venturi may comprise at least one first frusto-conical, frusto-pyramid or horn shaped body, optionally a cylindrical body, and an at least one second frusto-conical, frusto-pyramid or horn shaped body.

In one arrangement a gap may be provided between a divergent end of one first/second frusto-conical, frusto- pyramid or horn shaped body and an adjacent convergent end of one further first/second frusto-conical, frusto-pyramid or horn shaped body, the divergent end of the one first/second frusto-conical, frusto-pyramid or horn shaped body being smaller in diameter than the convergent end of the one further first/second frusto-conical, frusto-pyramid or horn shaped body.

Preferably the divergent end of the one first/second frusto-conical, frusto-pyramid or horn shaped body is substantially longitudinally coincident with the convergent end of the one further first/second frusto-conical, frusto-pyramid or horn shaped body.

In a preferred embodiment, the housing extends rearward of the rotor and acts as a diffuser, the housing diverging from the throat to a rear opening rearward of the rotor.

Preferably, the rotor supports at least two blades. Further preferably, the turbine has either 3 or 6 blades. It will be appreciated, however, that any number of blades of 2, 3, 4, 5, 6 or more can be used with the turbine.

Preferred embodiments of the present invention include raked or rearwardly-splayed blades, from the base to the blade tip by a tilt angle of about 1° to 20° from a plane perpendicular to the central axis to facilitate improved usable power generation from the turbine.

According to a fourth aspect of the present invention there is provided a method of generating power from water flow, the method including the steps of:

providing a central axis water turbine according to the first aspect of the present invention to a marine or river environment;

allowing water movement through the turbine to cause the blades to rotate; and

drawing usable power from the turbine.

According to a fifth aspect of the present invention there is provided a kit of parts for a central axis water turbine, the kit including: a power generator module comprising a central axis and a turbine body, a rotor mounted on the turbine body for rotation about the central axis, the rotor comprising a central hub for supporting a plurality of blades, the power generator module further including mounts for mounting one or more support struts and a generator in use driven by the rotor; a plurality of blades which include features of the first aspect of the present invention; a housing; a plurality of support struts for supporting the power generator module in a central position relative to the housing; wherein the housing, when in use surrounds the rotor

Preferably the housing includes support strut mounts for mounting support struts so that to install on site, the support struts may be readily assembled to extend between the power generator module and the housing.

Preferably the housing is in the form of a main body comprising a cylindrical bore within which the rotor and blades are disposed, the cylinder extending upstream of the blades when installed.

Preferably the blades are raked or splayed rearward or downstream from the blade root to the blade tip by a tilt angle of about 1° to 20° from a plane perpendicular to the central axis.

Throughout this specification, unless the context requires otherwise, the word “comprise”, or variations such as “comprises” or “comprising”, will be understood to imply the inclusion of a stated element, integer or step, or group of elements, integers or steps, but not the exclusion of any other element, integer or step, or group of elements, integers or steps.

Any discussion of documents, acts, materials, devices, articles or the like which has been included in the present specification is solely for the purpose of providing a context for the present invention. It is not to be taken as an admission that any or all of these matters form part of the prior art base or were common general knowledge in the field relevant to the present invention as it existed in Australia before the priority date of each claim of this specification.

In order that the present invention may be more clearly understood, preferred embodiments will be described with reference to the following drawings and examples.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 depicts a turbine blade having a twist angle of 70° in a number of views;

FIG. 2 depicts a 3D view of turbine blade (with the blade twist angle (β) and tilt angle or angle of inclination (γ) definition;

FIG. 3 depicts a 3D view of a turbine blade showing the twist;

FIG. 4 shows a graph of results of the efficiency of the turbine for various blade twist angles at different flow conditions;

FIG. 5 depicts a turbine body having six turbine blades;

FIG. 6 is a side elevation view of a blade showing the leading edge being a straight edge;

FIG. 7 is a front elevation view of a blade showing the blade tip markedly twisted so as to be presenting almost a flat face on a normal rotation sweep out of the page;

FIG. 8 is a detail view of a blade stem showing the direction of fibres laid longitudinally along the blade from root to tip;

FIG. 9 is a detail section view of a blade stem showing a connector sleeve which is held on with an interference fit;

FIG. 10 shows a plurality of section views along the blade from root to tip to demonstrate the twist along the length of the blade;

FIG. 11 depicts a side elevation section view of a central axis water turbine according to a preferred embodiment of the present invention;

FIG. 12 is a graphical display of power output of the turbine plotted against various rake or tilt angles at different flow conditions;

FIG. 13 is a side elevation section view of a central axis water turbine according to another preferred embodiment of the present invention;

FIG. 14 shows an isometric exploded view of a rotor of a water turbine according to a preferred embodiment of the present invention;

FIG. 15 a front elevation view of the central axis water turbine according to a preferred embodiment of the present invention;

FIG. 16 is a section view in side elevation of a central axis water turbine according to yet another embodiment of the present invention;

FIG. 17 is an isometric view of the central axis water turbine according to an embodiment of the present invention with the housing or cowling removed for clarity;

FIG. 18 is an isometric view of the central axis water turbine according to an embodiment of the present invention shown in an installed position on ballasted feet;

FIG. 19 is a front elevation view of the installed turbine shown in FIG. 18;

FIG. 20 is a plan view of the installed turbine shown in FIG. 18.

FIG. 21 is a side elevation view of the installed turbine shown in FIG. 18;

FIG. 22 shows a perspective view of a pair of mounted central axis turbines according to a preferred embodiment of the present invention;

FIG. 23 is a front elevation view of a housing showing tangentially-mounted support struts;

FIG. 24 is an isometric view of a housing showing mounts for support struts; and

FIG. 25 is an isometric view of a half-boot or half-plug for reducing interference drag at a blade/nose cone interface.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring to FIGS. 1 to 3, a blade for use in a fluid driven turbine is generally depicted at 24. As shown in isolation in FIG. 2, the blade 24 has a blade root 27, a blade tip 28, a leading edge 31 extending from the blade root 27 to the blade tip 28 and a trailing edge 33, also extending from the blade root 27 to the blade tip 28.

A blade root chord is defined as a straight line between the leading edge 31 and the trailing edge 33 at the blade root 27. A blade tip chord is defined as a straight line between the leading edge 31 and the trailing edge 33 at the blade tip 28.

In a preferred form, the blade is designed with a twist angle of approximately 70°, meaning that the tip chord of the blade is angularly displaced by an angle of approximately 70° relative to the root chord of the blade.

The optimum twist angle of approximately 70° was determined using computational fluid dynamics (CFD) modelling. The graph depicted in FIG. 4 shows the efficiency of the turbine for various blade twist angles at different flow conditions. The optimum points are when the efficiencies are at the highest at each speed. Various profiles and twist angles were investigated. It was discovered that the optimum twist angle for a marine turbine running at 27 rpm and having a housing with a throat diameter of 5.5 m was 70°.

This preferred twist angle is significantly different from that commonly employed in traditional turbine blade design. While the preferred twist angle must be optimized for particular turbines, twist angles of this magnitude can give significant improvements in turbine efficiency.

The blade design is able to capture the power from the incoming flow more uniformly, instead of the forces being concentrated at the tip. The twist angle also results in a high angle of attack at the root 27 and less of an angle of attack at the tip 28 (technically called “geometrical washout”). This also results in a better distribution of power absorption from root 27 to tip 28.

FIG. 5 shows six blades 24 installed on an exemplary turbine. However, the blades may be used in many different turbine designs, with any number of blades. The blades are particularly suited for use in a turbine having a housing defining a flow channel. Preferably the housing has a flow restriction and other preferred features are hereinafter described. Advantageously, this preferred arrangement increases the velocity of liquid flowing through the flow channel in a restricted part of the flow channel, relative to an unrestricted part of the flow channel. The flow restriction preferably comprises a venturi, which may form part or the entire flow channel. In particular, the venturi may comprise a divergent-convergent-divergent venturi, tapering from openings at either end of the flow channel towards an inner part of the flow channel.

Preferably the housing is substantially symmetrical about the central axis. The venturi may comprise at least one first frusto- conical, frusto-pyramid or horn shaped body, optionally a cylindrical body, and an at least one second frusto- conical, frusto-pyramid or horn shaped body. In one embodiment a gap is provided between a divergent end of one first/second frusto-conical, frusto-pyramid or horn shaped body and an adjacent convergent end of one further first/second frusto-conical, frusto-pyramid or horn shaped body, the divergent end of the one first/second frusto-conical, frusto-pyramid or horn shaped body being smaller in diameter than the convergent end of the one further first/second frusto-conical, frusto-pyramid or horn shaped body.

Preferably the divergent end of the one first/second frusto-conical, frusto-pyramid or horn shaped body is substantially longitudinally coincident with the convergent end of the one further first/second frusto-conical, frusto- pyramid or horn shaped body.

In a preferred embodiment, the housing extends forward of the rotor. It also extends rearward of the rotor and acts as a diffuser, the housing diverging from the throat to a rear opening rearward of the rotor. Preferably, the turbine has at least two blades. Further preferably, the turbine has either 3 or 6 blades.

FIG. 6 shows a blade which is constructed from glass- or carbon-reinforced substrate. The fibres of glass or carbon are laid so that they extend down the blade from root to tip for optimum strength/weight ratio. FIG. 9 shows a sleeve which is press-fitted onto a stub-axle extending from the blade. The sleeve then fits into a rotor bore which is disposed rearwardly or downstream, and preferably at a 5 degree angle so as to improve power output. The blade stub extends parallel to the blade leading edge.

Referring to FIGS. 11-25, a central axis water turbine assembly in accordance with a preferred embodiment of the present invention is generally indicated at 10 and comprises a main body 12, a rotor 14 and an optional housing or cowling 16. The main body 12 includes an electric generator assembly 18 and the rotor 14 is mounted for rotation on a shaft 20 about a central axis. The rotor 14 includes a hub 22 supporting a plurality of blades 24, the present preferred embodiment shown with six blades, each blade extending from a blade root 27 mounted on the hub to a blade tip 28. When installed, the housing 16 is disposed in a position so that an inner wall encircles the rotor 14 and in some embodiments converges from a front opening 29 forward of the rotor to a narrower throat 30 adjacent the rotor 14 to direct water flow towards the rotor 14. The blades 24 of the rotor 14 are raked rearwardly from the blade root 27 to the blade tip 28 by a tilt angle of approximately 5°, meaning that the leading edge 31 extends rearwardly from the blade root 27 to the blade tip 28 at an angle of approximately 5° to a plane 35 perpendicular to the central axis passing through the leading edge at the blade root 27.

Preferred tilt angles were determined using computational fluid dynamics (CFD) modelling. The graph depicted in FIG. 12 shows the modelled relative power output of a turbine for various tilt angles at different flow conditions. The optimum points are when the efficiencies are at the highest for each speed. This specifies that for the turbine to run at optimum efficiency under known conditions and design criteria, the blade should have a rearward tilt angle of between 1° and 20°, preferably about 5°. While the graph indicates that optimum efficiency may be achieved with tilt angles of greater than 5°, a tilt angle of no more than about 5° is preferable to minimise bending moments at the blade root under some mechanical configurations. However, with appropriate mountings, it is envisaged that tilt angles greater than 5°, say, up to 20° or more may be employed successfully.

In use, on some embodiments, when deployed in a current and generally parallel with it, water is directed by the converging cowling or housing 16 to flow toward the rotor 14. As the water flows past the blades 24, the rotor 14 is driven to rotate the shaft 20 about the central axis, which in turn drives the generator 18 producing electrical power output. The generator assembly 18 may be connected to a gearbox which in turn would be connected to the shaft, but in this preferred embodiment, the generator 18 is directly coupled to the shaft with a splined connection without requiring a gearbox.

The shaft 20 may be of any suitable material so as to resist corrosion in an aggressive environment and to support the loadings required. Carbon steel is preferred, however, other materials may be useful, including for example, stainless steel. Furthermore, for the same protective purpose, some exposed parts of the shaft are covered with a sleeve or sheath or other prophylactic material such as for example paint. Grease or other protective material such as for example barium dichromate or the like is packed or injected into the interstitial space between the sleeve and the shaft in order to facilitate further protection of the shaft.

In order to minimise interference drag, a plug 40 is provided around and/or adjacent the blade root 27 so as to smooth the flow of water in the region adjacent the blade root 27 and hub. The plug 40 may be constructed from polyurethane and may be in the form of a flexible boot or a sealant/adhesive fluid which to install is pumped into place. The preferred plug 40 is shown, or one half of it, at FIG. 25.

The hub 22 is affixed to the shaft with an interference fit so as to simplify its connection to the shaft but also to maintain security of that connection.

Support struts 50 are connected to the cowling or housing 16 so as to support the main body 12 and rotor in a substantially central disposition in the cowling and/or housing 16. Any suitable number of support struts 50 may be used, and in the Figures shown, there are three. The support struts 50 may be hollow so as to house reservoirs of material such as for example grease, air or hydraulic fluid, or to form ducts for the passage of electrical cables or hydraulic oil lines and the like. The support struts 50 shown in FIGS. 1 and 5, for example, radially extend from the generator and rotor.

Furthermore, the support struts 50 rotatably support the shaft 20. Two spaced-apart bearings are used, one upstream 51 and one downstream 53, interconnected by a bearing sleeve. The support struts 50 connect to the bearing sleeve at their outer diameter.

A brake 60 is provided, which in the preferred embodiment shown, is disposed adjacent the support struts. The brake 60 is preferably a fail safe mechanism, wherein pressure, preferably hydraulic, is used when the turbine 10 is in use to hold a brake shoe or a resistance element such as for example a magnetic or pneumatic element, against an engagement force, out of engagement with the shaft 20. If there is a failure condition such as a blade loss, breakage, or electricity cut, or some other problem, the power to the brake is cut, either slowly or quickly, so that the engagement force drives the brake shoe or braking element into engagement or activation with the shaft 20 to slow or stop the shaft 20 and rotor 22.

FIG. 13 is an exploded view of a preferred turbine main body 12 and rotor 14. The main body 12 houses the generator 18 which is directly connected to the shaft 20 via a splined connection. The generator 18 which in the embodiment shown is an induction motor or permanent magnet motor, which, in generator mode, is used to convert the mechanical power output from the rotation of the rotor to electrical power. Mechanical torque is supplied by the rotating blades 24 to the shaft 20, which induces a voltage at the stator output terminals. Conventionally, induction motors have a variable rotor flux, provided from an external source. This flux interacts with the stator flux and the difference between the rotational frequencies of the two determines the mechanical torque or induced terminal voltage when operating as a motor or generator respectively.

Six blades 24 are mounted on the hub 22 of the rotor 14 and may be blades 24 having a twist angle in the order of 70° as depicted here. However, blades 24 of many different shapes and configurations can be used for the turbine 10, without departing from the spirit or ambit of the invention. The blades 24 can be manufactured from a mould process using fibre reinforced plastics or other compounds such as carbon fibre reinforced plastics, but can alternatively be fabricated using structural ribs and sheet skin from steel, non-ferrous alloys or fibre reinforced plastics. Fibre direction at the root 27 is longitudinal as shown in the Figures, in order to improve strength at that critical point.

A nose cone 65 is mounted on the front of the hub 12 of the rotor 14 to reduce drag on the rotor 14 and to promote flow attachment. The nose cone 65 can be fabricated from a variety of materials, including but not limited to fibre reinforced plastics, other composites or steel. The nose cone may be solid, but in the preferred embodiment shown, is hollow and may provide space for reservoirs such as for example grease tanks. A tail cone may also be provided and may have the same functionality as the nose cone, in the preferred embodiment, being as shown in the drawings. Preferably, a grease tank and dosing unit are provided, disposed on an upper portion of the housing, outside the throat and blades so as not to interfere with the water flow from which usable energy is extracted.

FIG. 22 shows two turbines 10 deployed on a pylon 67. The turbines 10 may also be deployed by other means such as but not limited to; gravity based structures or floating structures. The structures may or may not afford axial rotation around the vertical axis. The turbine housing shown in the Figures is constructed of modular components that will generally be manufactured from moulded fibre reinforced plastics in sections that are then joined together with structural fasteners. The turbine housing can alternatively be fabricated using structural ribs and sheet skin from steel, non-ferrous alloys or fibre reinforced plastics. The housing allows focussing of water into the turbine from currents that are not perpendicular to the plane of rotation of the blades.

For commercial purposes, the turbine 10 can be any size. As an example, it is expected that a turbine of five meter diameter at the blades and approximately seven meters at the housing mouth, is capable of producing up to approximately 1 MW depending on water speed. The generator unit may produce electrical power as either alternating current (AC) or direct current (DC), and may be controlled electronically, which may allow control of electrical power output characteristics.

Power generated by the generator means may be stored by or separately from the generator means, for example, by one or more batteries, or may be fed directly into a power system, for example, a local power system. In the latter case, synchronisation, power factor and voltage of the power generated may be regulated electronically, using a variable speed drive (VSD) for example, prior to being fed into a local power distribution mains system such as a power grid. The generator means may be coupled by a cable, for example, a submarine cable, to the local power distribution system.

As mentioned, the cowling, housing or duct 16 in preferred embodiments has a liquid or fluid flow channel therethrough and the rotor 14 is mounted in the flow channel for rotation in response to liquid/fluid (water) flow through the flow channel. The flow channel defines a flow restriction which can form a venturi comprising a convergent-divergent venturi, tapering from openings at either end of the flow channel towards an inner part of the flow channel. The housing is substantially symmetrical about a mid-point location and the rotor is located substantially at the mid-point location within the flow channel.

The housing or duct or cowling 16 comprises a single sleeve. In such implementation the housing or duct has a narrowed or reduced waist on an outer surface thereof between ends thereof, and in this case, substantially mid-way between the ends thereof. However, in a modified implementation the turbine housing can comprise an outer housing sleeve and an inner housing sleeve which inner sleeve defines the flow channel. In use the housing can be secured to an underwater surface by a support or mounting structure and substantially aligned to a direction of predicted tidal or current flow. The angle between the actual direction of the housing and the direction of tidal or current flow can be between about 0° to about 45° or more. The housing, as shown in the Figures, comprises sections, each of which includes flanges at their perimeters so that bolts or other fasteners such as for example adhesive tapes or glues can be used to hold them against their adjacent component.

Testing has shown that, as shown in the Figures, power output from the turbine unit increases when the inlet radius is larger than the throat radius. Testing and modelling has indicated that power is increased to an optimum level when balanced against drag, when the inlet radius is approximately 10% larger, however other ratios may be used such as 20% or 30% which is expected to increase power output.

An inlet and/or outlet diameter of the flow channel can be in the range 1 metre to 25+ metres, depending on the amount of power generation required. Typically, the turbine will have a diameter of around 2 to 10 metres. The length of the flow channel or duct can be in the range 1 metre to 15+ metres, depending on the size of the turbine.

The turbine housing 16 is preferably secured to an underwater surface, for example, a floor or bed of a sea, ocean or river by, for example, a mounting structure, which may be substantially aligned with the direction of tidal flow. Alternatively, the turbine housing 16 may be moveably secured to an underwater surface to allow movement to face the direction of main or tidal flow. The turbine unit may comprise a sub-sea turbine, but it will be appreciated that the turbine unit may be used in any underwater environment where a liquid flow exists, for example, in any tidal or river flow situation.

An electrical cabinet 69 is provided in the preferred embodiment shown in the Figures, the cabinet being affixed to the downstream end of the generator 18. The generator chamber is sealed from the electrical cabinet with positive air or hydraulic fluid pressure.

Referring to FIG. 23, the support struts 150 are tangentially-mounted to improve torque transfer between generator and housing. This preferred arrangement is advantageous because it can facilitate reduction of the size of the struts, and reduces shadowing of the support struts. That is, it can be seen that radially-extending support struts 50 (FIG. 5) can be completely shadowed behind a radially-extending blade, each time they pass a strut 50. However, this shadowing is more gradual with a tangentially-extending blade, which also assists with improving exit flow from the trailing edge of the blade.

In some preferred embodiments, the electric generator assembly 18, cabinet 6 a, broke and hub and rotor can be assembled as a single module. The module (not shown) includes the rotor, shaft, generator, brake, hub and other associated elements suitable for mounting in the centrally-disposed module. The module is streamlined and may be shipped separately such as for example in a kit of parts. The housing may be shipped as shown in FIG. 14, wherein the mounts for the support struts are welded to the inner wall of the housing. The support struts are then bolted to the wall mounts and then bolted to the tangential module mounts so the module is held in place in its central position by the support struts and bolted in place. Thus, a kit of parts may be supplied to a site, whereupon the kit is assembled by simple bolted connections on, say, a barge, and then is installed at sea or other water flow site such as a river.

The marine environment is extremely aggressive to materials from which the turbine assembly is constructed. Therefore several measures are taken in the preferred embodiment shown to mitigate damage to the turbine assembly. For example, the housing 16 and main body 12, and various other parts are painted or otherwise coated with antifouling material to minimise growth of marine life including barnacles and other sea creatures. Furthermore, sacrificial anodes (not shown) are attached to metal components or otherwise electrically connected thereto.

Preferably the power generator generates electrical power.

The turbine may also be adapted to run a pump which in turn causes a generator to rotate to generate electricity through fluid being pumped by the turbine.

The turbine includes a housing having a flow channel there through, the at least one turbine means being mounted in the flow channel for rotation in response to liquid flow through the flow channel. The generator means may be located separately from the turbine housing or integrated in the rotor.

Preferably the liquid is provided from a body of water within which the turbine unit is submerged, and may be sea water or river.

It will be appreciated by persons skilled in the art that numerous variations and/or modifications may be made to the invention as shown in the specific embodiments without departing from the spirit or scope of the invention as broadly described. The present embodiments are, therefore, to be considered in all respects as illustrative and not restrictive. 

1. A blade for driving an underwater power generation machine, the blade in use being adapted for rotation about a rotation axis in response to water flow from a selected direction, the underwater power generation machine being adapted to be mounted in a body of the water and having a power generation unit adapted to be driven by the blade so as to generate power, the blade comprising: a blade root; a blade tip; a leading edge extending from the blade root to the blade tip; a trailing edge extending from the blade root to the blade tip; a blade root chord defined as a straight line between the leading edge and the trailing edge at the blade root; a blade tip chord defined as a straight line between the leading edge and the trailing edge at the blade tip; wherein the blade tip chord is angularly displaced from the blade root chord by a twist angle of between 50 degrees and 90 degrees.
 2. The blade according to claim 1 wherein the blade tip chord is angularly displaced from the blade root chord by a twist angle of about 70 degrees.
 3. The blade according to claim 1 wherein the blade is constructed from a fibre reinforced plastics.
 4. The turbine blade according to claim 3 wherein a plurality of fibres from the fiber reinforced plastic extend along the length of the blade.
 5. An underwater power generation machine including a blade according to claim
 1. 6. A central axis underwater power generation machine including: a turbine body having a central axis; a rotor operatively mounted on the turbine body for rotation about the central axis, the rotor comprising a central hub supporting a plurality of blades, each blade being in accordance with claim 1 and extending from a blade root mounted on the hub to a blade tip; and a generator driven by the rotor.
 7. A central axis underwater power generation machine in accordance with claim 6 further comprising: a housing surrounding the rotor and adapted to direct water flow towards the rotor.
 8. The machine in accordance with claim 6 wherein the leading edge of the blades are tapered, raked, tilted or splayed rearward or downstream from the blade root to the blade tip by a tilt angle of about 1 degree to 20 degrees from a plane perpendicular to the central axis.
 9. The machine in accordance with claim 7 wherein the housing converges from a front opening forward of the rotor to a narrower throat adjacent the turbine body.
 10. The machine in accordance with claim 9 wherein the leading edge of the blades are splayed rearward from the blade root to the blade tip by a tilt angle of 2 degrees to 10 degrees.
 11. The machine in accordance with claim 9 wherein the leading edge of the blades are raked within a range of 4 degrees to 6 degrees from the plane perpendicular to the central axis. 